Driving mechanism



my #al E46. D. H. HEYNAU DRIVING MEGHANISM Filed Oct. 12, 1942 5 Sheets-Sheei'l l Faas July 30, 1946. D. H. HEYNAU DRIVING MECHANISM `5 sheets-sheet 2 Filed Oct. 12, 1942 NE, o@ ll. jf o mf Mm *Gx NU @n o l! @.bb Q NNCWM. V A W ws www @W /A v, W Mw, Olmk v al.

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D. H. HEYNAU DRIVING MEGHANISM 5 heets-sneet 5 Filed Oct. l2, 1942 Patented July 30, 1946 UNITED STATES PATENT OFFICE 6 Claims.

This invention relates to a power transmission unit for transmitting power from the prime mover to a load and more particularly to a variable speed power transmission unit.

An object of this invention is to provide a power transmission unit wherein the speed of rotation may be varied and reversed at the will oi the operator without shifting gears.

Another object of this invention is to provide a control mechanism for controlling a variable speed and reversing mechanism easily and efciently at the will of the operator.

Another object of this invention is to provide a multiple power transmission unit transmitting power from a common prime mover to several loads, either independently or simultaneously at various speeds, the speed of one unit differing from the speed of another unit.

Another object of this invention is to provide a control unit for controlling the movement of a gun at the will of the gunner, which gun is power driven.

Another object of this invention is to provide a pair of power transmission units responsive to a common prime mover, one of which units may be used in elevating the gun and the other in rotating the gun horizontally.

Another object of this invention is to combine a .power transmission unit utilizing a planetary gear system wherein the relative speed of the gears may be changed in either direction, to thereby control the output speed and direction of rotation.

Another` object of this invention is to provide a variable speed and reversing unit driven by a uni-direction constant speed prime mover` Another object of this invention is to provide a manual control for a variable speed and reversing mechanism wherein equal increments of movement at the control are translated into unequal increments of movement at the variable speed reversing mechanism.

Another object of this invention is to provide a control for a variable speed reversing mechanism such that predetermined increments of movement of the manual controls at low speeds result in a slight change in speed ratio and the same increments at high speeds greatly change the speed of the device.

Other objects and advantages reside in the construction of parts, the combination thereof and mode of operation, as will become more apparent from the following description.

In the drawings:

Figure 1 discloses a schematic cross sectional view of the preferred embodiment of the speed control mechanism used in supplying power for actuating a gun.

Figure 2 is a longitudinal cross sectional view of the variable speed control mechanism, taken substantially on the line 2--2 of Figure '7.

Figure 3 is a fragmentary perspective View of the lever, the bushing controlled thereby and the conical member removed from the housing.

Figure 4 is an exploded View of the bushing control mechanism.

Figure 5 is a diagrammatic end View of one bushing and its control mechanism to show the nature of the cavities therein.

Figure 6 is an exploded view of the differential mechanism.

Figure 7 is a cross sectional view of the variable speed control mechanism, taken substantially on the line '1 1 of Figure 2.

The control mechanism for the gun includes a cage that is rotatably mounted with the gun, which cage supports the driving mechanism, the necessary controls and the gun, as will appear more fully from the description of the device that will now be made.

Referring to the drawings, the reference character It indicates a wall of a fuselage, wing or some other portion of an airplane provided with an annular opening. superimposed upon and attached to the margin of the wall lll is an annular, internally toothed gear ring II. The gear ring il and the inner margin of the wall lll cooperate to form an annular channel opening inwardly. A cage l2 is carried in the opening in the wall l0. This cage l2 is provided with an annular outwardly directed flange i4, projecting into the channel formed between the inner margin of the wall lllrand the internally toothed gear ring Il. The flange I4 is mounted'upon suitable roller bearings I6 and I8 disposed upon opposite sides of the flange and engaging the wall l0 and the gear ring Il respectively. Although member H has been referred to as a gear ring, a gear sector or gear sectors could be used for some types of installations.

A prime mover 2l), such as an electric motor, is mounted in one end I9 of the cage l2, which end may -be referred to as the bottom of the cage, as viewed in Figure 1. The cage need not necessarily be arranged so that the lower end shown in Figure 1 is always at the bottom, as the gun in some installations may be mounted below the cage, in which event this end would then be the top of the cage, or the gun may be mounted so that this particular end could be referred to as the vertical 3 end of the cage. In other words, the cage is mounted opposite the gun, irrespective of the particular location of the gun.

This prime mover 2c may consist or" an electric motor energized from a suitable voltage source. If, for example, the available voltage is 12 volts direct current, then the ,prime mover would be a l2 volt D. C. electric motor. This prime mover may be set to rotate at a constant speed in one direction and the same direction at all times when in use.

A pair of reversible, variable speed transmission units 39 are mounted on either side of the prime mover or electric motor 25, one on each end. 'As these reversible, Variable speed transmission units are identical, only one will be described in detail.

As may best be seen by referring to Figure the reversible Variable speed transmissionunit St includes a housing 32. This housing enclcses a plurality of conical members 34, 3S, 38 and te arranged in pairs rotatably connectedfthrough a rigid, metallic ring M. The conical members 3i and 35 constitute the driving unit for thering driving the conical members 33 and liti.

The relative speed of the two pairs of conical members is dependent upon their adjustment. The-conical members 34 and 38, are mounted for rotation without axial adjustment. conical member of each pair, namely 355 and 4t, are mounted for axial adjustmenaas will appear more fully from the detailed description that folV- lows.

Conical member v3ft' is integral with a tubular sleeve 42 splined to a shaft 59 that is either integral with or connected to the rotor shaft 22. The tubular sleeve 42 is journalled in a bearing 52 and the end-thrust bearing 54, the end-thrust bearing having the inner race arranged to abut the conical member t, so as to prevent axial movement thereof. The conical member 38is also provided with a tubular sleeve 53 mounted on a splined shaft S. vThe tubular sleeve 53 is journalled in a bearing e2 and an endfthrust bearing Sli, the inner race of which abuts the top'of member 38. The bearings 52, 54, 62 and Fili are press-fitted or otherwise secured inV position in the cavitiesfound in the housing 32. The end-thrust bearings 5t and 64 abut suitable shoulders that provide solid mountings for these bearings. Y

In order to provide adjustment for the conical members 36 and 4G, each of these members is mounted for axial adjustment. The conical member 35 is integral with a tubular sleeve lil splined upon the shaft Sii and journalled in bearings ?2 and` 1Q, of which the latter is an endthrust bearing. The bearings i2 and l are not fixedly secured to cavities in the housing 32; but instead. are mounted in an adjustable Ybushing 'i6 mounted for axial movement parallel to theV longitudinal axis of the shaft i. lThe conical member Mi is integral with the tubular sleeve Sil, splined upon the shaft t0, and journalled in bearing 82 and 84, of which the latter is an endthrust bearing. The bearings S2 and 84 are fixedly mounted in a tubular bushing S6 mounted for axial movement in the housing 32.

In order to change the relative speed of the pairs of conical members, the bushings it and 86 are' adjusted axially in unison. Thus, it is possible to increase the distance between conical members 34 and 36 and at the same time adjust The other cal members, the speed of the metallic ring 4| is changed. Thus, by rotating the conical members 3d and 36 at a constant speed, it is possible to rotate the conical members 38 and Ml at a higher or a lower speed, depending entirely upon the adjustment of the conical members. The mechanism for adjusting the conical members will no'w be described.

An adjusting lever |90 is mounted on a shaft |62, which shaft is pivotally mounted to the housing 32. This lever is bifurcated and provided with apair of arcuate slots |04, one in each bifurcation lima and mtb. The centers of curvature of the slots IEM are displaced from the axis of the shafts |532, so that as the lever |99 is oscillated, a pair of pins |86, actuated by the slots IM, have a longitudinal movement parallel to the axis of the shaft El). Each pin |06 has one end iixedly attached in the bushing 85, there being one pin it mounted on each side of the bushing, so that as the lever |539 is oscillated' about the pivot |92, the'bushing 85' moves to the right or to the left, as viewed in Figure 2. Since there' are two diametrically disposed pins |96, it reduces twisting movements.

. directed near the target, when it may be adjusted slowly to keep it directed on the target.` Y

In order tocau'se bushing i6 to be adjusted in unison with the bushing 85, these two bushings are interconnectedrby a connecting rod which will now be described; Bushingl member 85 is provided with a cut-away portion or notch Il!) reconical members 38 and it toward each other.

If members Se and 36 are adjusted toward each other, members 38 and it should then be separated. By changing the adjustment of the coni- Vbeen indicated schematically in Figure 5.

ceiving a projection'llZ located between notches Ill and I3 and integral with a tubular sleeve H4 mounted upon a reduced end of a pin H5, provided with an enlarged end having cut-away portions ||8 andV |20, leaving an'exteneion |22. The exten-sion |22 projects into a suitable notch |24 in bushing member 1E.v The cut-away portions or notches HEI, ||"|,v|l3, H8, |29 and |213 arejprovided with arcuate bottomsrthat have a Vcurvature corresponding to the complementary part of the adjacent Ymember. The' radii or" notches ll'and |24 are concentric with the longitudinal axis of the pin H6 and substantiallyv concentric with the axis of rotation of the ring 4|. The curvatures of notches Il! and H3 are centered on the axis of rotation of conical 'member 40. The curvatures of notches H8 and |25 are centered on the axis of rotation of the conical member 36. For the purpose of illustration, the bottoms of some rof the cut-away portions have This arrangement causes the bushings 16 and 85 to be moved in unison. Due to the fact that the conical members 36 andv 45 are diagonally disposed, or located upon opposite sides of the ring 4|, it can'be readily geen that as these conical members are adjusted-to the right or to the left, as viewed in Figure 2, one willbe moved away from and the other toward the other'conical member of the pair, or vice versa. This causes the ring 4| to be seated between the conical members and contacting the conical members, .irrespective of the relative adjustment of the conical members.

A suitable compressible washer or spacing member |30 is located between the shoulderv |32 on the'. pin H6 and the tubular sleeve H4. In-

stead of a compressible washer being used, a rigid washer of suitable size either with or without shims as required, may be used. In order to tighten or loosen the pressure exerted by the conical members against the lbevelled inner periphery of the driving ring Lil, it is merely necessary to adjust the lock nuts |313, threadedly engaging the end of the pin |8. The use of the tubular sleeve im in addition to permitting adjustment, also facilitates assembly of the parts.

The connecting unit has been centrally positioned in the plane formed by the axis of rotation of the shaft 5D and the axis of the shaft 60. By mounting the connecting unit in this central position, theY bearings may be easily adjusted. This connecting unit, consisting of the tubular sleeve I4 and a pin H6, is actuated by the movement of one bushing in a direction parallel to the movement of this bushing and parallel to the movement of the other bushing. This tends t re duce torque and twisting movement. Furthermore, the central location of the connecting unit is a direct method of interconnecting the bushing and the adjustable conical members, thereby obtaining a direct, rigid connection between the bushings. It can readily be seen that a symmetrical arrangement of parts is thereby obtained to great advantage.

The shaft 50 has splined on its outer end a sun gear |59 meshing with a planetary pinion |52 journalled on a pintle |54 carried on a spider |58 that has fixedly attached thereto a drive shaft |66. The outer end of the shaft 5B has splined thereto a gear |62 meshing with the external gear teeth |66 of a ring gear |54, having its internal gear teeth meshing with the pinion |52.

When the velocity imparted by the sun gear |50 to the planetary pinion |52 is equalled and opposite in direction to the velocity imparted by the ring gear IEil, the axis of the planetary pinion |52 journalled on the spider |56 stands still. This causes the spider and the output shaft |60 to stand still. This condition exists at a predetermined relative speed ratio of the shafts 50 and 60. This speed ratio will zbe referred to as the critical speed ratio. Whenever this speed ratio is reduced, the spider |56 will rotate in one direction and whenever the speed ratio is increased, the spider will rotate in the opposite direction. The gear ratios may be so selected that the critical speed ratio of the speed of the shafts 5D and 6|) occurs when the conical members of both pairs are equally spaced so that by separating the driving conical members, the spider rotates in one direction and vice versa. This permits the reversal of the speed changing unit. By selecting the proper gear ratios, the critical speed ratio may be one or unity. If so, the spider will stand still whenever the shafts 5E] and 68 rotate at the same speed. In the event the shaft 60 rotates at a faster speed than the shaft 50, the spider will rotate in one direction and when the shaft G0 rotates slower than the shaft 5t, the direction of rotation o-f the spider will be reversed. This one to one ratio of the shafts 52 and S0 has merely been selected for the purpose of explanation, as it is not necessary for the operation of the reversible, variable speed unit to select a critical speed ratio of one.

As may best be seen by referring to Figure 6, the spider |56 is provided with a plurality of openings receiving the pinions |52. The end Ia of the spider is journalled in a pair of bearings |79 and |12. Ihe bearing |18 is Xedly mounted in the housing 32. The bearing |12 is mounted in the ring gear |64. The opposite end of the spider |55 is journalled in a pair'of bearings |16 and |3D. The bearing |76 is mounted in the ring gear |64 and the'bearing |85 is mounted in the housing |82 enclosing the differential mechanism. A bearing |84 is mounted within the spider |56 and supports the outer end of the shaft 50.

The output shaft |69 of the reversible, variable speed unit mounted to the right of the prime mover is xedly attached to the spider |56 and is connected through a suitable coupling unit 28) to a drive shaft 202 projecting into a speed reduction gear box 22d, provided with a drive shaft 206 suitably journalled at 208 and 2|il to the side wall of the cage I2, and carries a gear 2 I2 meshing with the inwardly directed gear teeth on member The control lever |20 is driven through a shaft 22|! attached to one of the shafts |02, which control lever is provided with a crank or lever 222 actuated by the gunner seated in a seat 22e. It is merely necessary for the gunner to actuate the lever 222 to the right or to the left to rotate the gun 226 mounted on top of the cage I2, as viewed in Figure 1, either in a clockwise or a counterclockwise direction, depending entirely upon the movement of the control lever 222.

The reversible variable speed unit 35 mounted to the left of the prime mover, as viewed in Figure 1, has the output shaft |65 rotating a drive shaft 282 projecting into a speed reduction gear box 204, identical to the one already described. The output shaft 2&6 of this second unit has its upper end terminating in a worm gear 230, meshing with a worm gear sector 236, raising and lowering .the gun in response to movement of the lever 222 shown to the left of Figure 1. Thus, it is seen that the angular position both horizontally and vertically may be adjusted from the same prime mover rotating at a constant speed, without changing gears, but merely changing the relative speeds of two rotating shafts.

The device disclosed herein has merely been shown for the purpose of illustration. The arrangement of parts may be altered and the mechanism changed so as to carry out the same fundamental principles. Instead of utilizing a mechanica1 control device, such a control device may be hydraulic or possibly electrical.

The device is easily controlled. Instead of utilizing separate control levers, a single control lever or pair of control levers moving in unison may be used, for example, such that the horizontal movement rotates the gun horizontally and the vertical movement raises or lowers the gun, as viewed in Figure 1. As a matter of fact, these movements may be so arranged that the handles point in the direction of the target. Both units may operate simultaneously, causing the barrel of the gun to swing through a diagonal path, depending upon the relative speed of the two units. By this arrangement, it is possible to keep the gun aimed at the target, irrespective of the relative movement of the .target with respect to the gun. When the target is passing rapidly within the range of the gun, the gun may be moved rapidly. When the target is moving more slowly, the movement of the gun may be reduced. In the event a target lmexpectedly enters the range of the gun, but the gun is directed in some other direction, the gunner may rapidly swing the gun at a high speed into position to be aimed at the newly discovered target.

Due to :the 'fact 'that Y'in .aircraft Vwari'are'tlfieY target `may be'within the range fof theigunfor a .period equal to :afraction :of a'minuta'it can readily be appreciated that it is very important that'fthe driving mechanism be adapted to rapidly swing the gun into position, Vbut atth'e same time to'permitslow movement of thegun .to keep iton'the'target. .It is Vpossibleto do so by the driving mechanism shown herein.

.In the :embodiment shown herein the prime moverfand the `.reversible variable speed :units have been *mounted upon Vthe end wall of the Y cage. ,The prime mover `and the reversiblevariable .speed :units maybe mountedelsewhere within the '.cage, or for thatlmatter, on .the outside .of the cage, whichever'may prove themost advantageous for v.the :particular `gun mounting and available parts 'and space. Ilurtliermore, the prime mover and the reversible lvariable .speed units :maybe mounted outside Vof .the cage, so thatone reversible variable speed unit will .actuate an external ,gear on the cage'for. horizontal movement, as viewedin Figure 1, and the other reversible variable speedunit may drive a shaft extending Vup through the center'of the cage,so as to actuate the elevation of the gun. rThe controls could then `be .brought up `through '.thecenter ofithe cage by suitable links and connecting' units, so that the Voperator could control `the units independently'of themovement ofthe cage. This arrangement would `serve to .reduce .the weight ofthe cage proper thathasetobe moved, thus, reducing the required power. Furthermore, for .some installations, Athe .Cage may 4be eliminatedin its entirety, the reversible variable speed units being vused to actuate the gunperse and the parts carried thereby.

Although the preferred .modiiication of vthe device has been described, it will be understood that within `the purview of thisinvention .various changes may be made inthe form, details, ,pr.oportion and arrangement or parts, .the combination thereof and mode of operation, which generally stated consist in va device capable of carrymr ing out the objects set forth, as disclosed and-'defined in the appended claims.

, Having thus described my invention,.I claim:

l. `A driving mechanism for transmitting various movements to driven means, said .driving mechanism including a .pair of variable -speed driving means, each cfsaid driving'means includingla Vpair of coaxially mounted .conical Vdriving members, a second pair of coaxially mounted conical driven members, one of the conical members of each pair being adjustably mountedfor axial adjustment, a drivingringlfor transmitting power from the conical driving members to the conical driven members, each of 'the adjustably mounted conical members terminating in aY tubular sleeve portion, a pair of tubular bushings mounted for axial movement, said bushing o'f oneof the conicalmembers being located on one side of the driving ring and the bushing of the other-conical member being located onthe opposite "side ofthe driving ring, "and connecting means including a notched tubular memberfsaid connecting means holding thebushings in xed spaced'relation 'from each othenso that as one bushing is adjusted and with it its conical memberfthe other bushing is'adjusted and with it its conicalmember, saidconnecting member having its longitudinal axis 'positioned in aplane determined by the Yaxes of rotation of :the conical members and .substantially.coincidental with the axis of rotation of the driving ring so as tofcause axial adjustment, va drivingring fortransmitting power from the conical `driving members to the conical driven members, a pair of :tubularbushings mounted for axial movement, .one of the .tubular bushings Vbeing coaxially disposed with respect to the conical driving'members one of which is .journalled in said bushingiorm'ovement therewithVsaid one bushing being located for axial-adjustment on one'side of the yringthe other tubular lbushing Ybeing c'oaxially Vdisposed with 'respect tothe conical driven members, Yone of'whichijs journalled therein .for axial movement therewith, said'one bushing being located on the opposite side of the ldriving ring, saidV bushings being provided with notches opening so as to be directed in the generalY directionof the axis-of rotation of the drivingiring, and con'- necting means including a cylindricalfc'onnecting member for interconnecting the bushings, said cylindrical connecting member including cut-- away portions on fopposite sides of extensions projecting into'said' notches, so Vthat `a'srone bushing is adjusted theother bushing is adjusted 'in the same direction, to thereby Aadjust the two conical members journalled in the bushings in unison to changethe relative speed of the driven' members with respect to the driving members.

3. A driving mechanism for transmitting various movements to driven means, said vdriving mechanism including 'a pair vof variable speed drivingmeans, each of said driving means including a pair .of coaxially mounted conical driving members, a second -pair -of coaxially mounted conical driven '-members, one of vthe conical members of -each pair being fadjustably mounted for axial adjustment, la driving ring for transmittingpower from the conicalrdriving members to the conical driven 'members la pair of tubular 'bushings mounted for `axial movementf'one of the tubular bushingsbeing'coaxially disposed with respect to the conical driving members `and located for axial adjustment -on one-side of the ring, the other tubular bushing being coaxially disposed with respect 'to the conical driven members and located on the oppositeside of the driving ring, each ofthe ad- Vjustablerconical members terminating in a tubular-sleeve journalled in one-of said bushingsrfor axial adjustment therewith, said bushings being provided with notches openingso as 'to bedirected=in`thegeneral direction of the axisl of rotation of the drivingring, andconnecting means provided with vextensions Vprojecting into said notches, said connecting .means'including `a pin and 'a sleeve mountedupon the pin, saidpin having :an extension projecting into .one of ',.the notches of one bushing iand the sleeve vhavingran extension projecting into thenotch of the other bushing, said sleeve being fixedly mounted upon the pinso .that as. one bushing is adjusted. axially the vother .bushingtis adjusted in like manner.

. 4. A driving mechanism for transmitting various 'movements to Vdriven means, said driving mechanism including a pair of -variable speed driving imeans, eachfof -said driving :meansincluding a pair of conical driving members, a second pair of corneal driven members, one of the conical members of each pair being adjustably mounted for axial adjustment, a driving ring for transmitting power from the conical driving members to the conical driven members, a pair of tubular bushings mounted for axial movement, one of the tubular bushings being concentrically disposed with respect to the conical driving members and located for axial adjustmentJ on one side of the ring, the other tubular bushing being coaxially disposed with respect to the conical driven members and located on the opposite side of the driving ring, each of the adjustable conical members terminating in a tubular sleeve journalled in one of said bushings for axial adjustment therewith, said bushings being provided with notches opening so as to be directed in the general direction of the axis of rotation of the driving ring, connecting means provided with extensions projecting into said notches, said connecting means including a pin and a sleeve mounted upon the pin, said pin having an extension projecting into one of the notches of one bushing and the sleeve having an extension projecting into the notch of the other bushing, said sleeve being fxedly mounted upon the pin so that as one bushing is adjusted axially the other bushing is adjusted in like manner, and means for axially adjusting the tubular sleeve upon the pin to thereby adjust the relative distance between the bushings.

5. A driving mechanism for transmitting various movements to driven means, said driving mechanism including a pair of variable speed driving means, each of said driving means including a pair of conical driving members, a second pair of conical driven members, one of the conical members of each pair being adjustably mounted for axial adjustment, a driving ring for transmitting power from the conical driving members to the conical driven members, a pair of tubular bushings mounted for axial movement, one of the tubular bushings being concentrically disposed With respect to the conical driving members and located for axial adjustment on one side of the driving ring, the other tubular bushing being coaxially disposed with respect to the conical driven members and located on the opposite side of the driving ring, each of the adjustable conical members terminating in a tubular sleeve journalled in one of said bushings for axial adjustment therewith, said bushings being provided with arcuate notches having a common center of curvature, cylindrical connecting means for interconnecting said bushings, said connecting means having arcuate cut-away portions on one side centered on the center of rotation of one pair of conical members and arcuate notches on the opposite side centered on the center of rotation of the other pair of conical members, the cut-away portions on the connecting means complementing the cut-away portions on the bushings, so that the bushings are interconnected through said connecting means so that as one bushing is adjusted axially the other bushing is adjusted in like manner.

6. A driving mechanism for transmitting various movements to driven means, said driving Ymechanism including a pair of variable speed driving means, each of said drivingV means including a pair of conical driving members, a second pair of conical driven members, one of the conical members of each pair being adjustably mounted for axial adjustment, a driving ring for transmitting power from the conical driving members to the conical driven members, a pair of tubular bushings mounted for axial movement, one of the tubular bushings being concentrically disposed with respect to the conical driving members and located for axial adjustmentl on one side of the driving ring, the other tubular bushing being coaxially disposed with respect to the conical driven members and located on the opposite side of the driving ring, each of the adjustable conical members terminating in a tubular sleeve journalled in one of said bushings for axial adjustment therewith, said bushings being provided with arcuate notches having a common center of curvature,

cylindrical connecting means for interconnecting said bushings, said cylindrical connecting means including a pin having arcuate notches on one side having a common center on the axis of rotation of one set of conical members, an adjusting sleeve mounted on the pin, said sleeve having arcuate notches centered on the axis of rotation of the other pair of conical members, the portions between the notches on the pin being seated in the notches of the adjacent bushing, the portions between the notches on the tubular sleeve being seated in the notches of the other bushing, means for adjusting the tubular sleeve on the pin to thereby adjust the distance between the bushings, and means interconnected to one of the bushings for shifting the bushings axially in unison to change the relative speed of the conical members.

DAVID HANS HEYNAU. 

